Positive displacement rotary pump and drive coupling therefor

ABSTRACT

A progressing cavity, positive displacement rotary pump assembly for fluid or semi-fluid material. The assembly includes a rotary shaft with an associated drive motor and pump components including a tubular stator with an interior helical surface and an orbital rotor within the stator operably connected to the shaft and having an exterior helical surface. The helical rotor surface has one more thread than the helical stator surface which it engages, to define sealed pumping cavities that advance axially as the rotor rotates and orbits within the stator. The rotor is coupled to the shaft by a flexible torque tube with one end connected to the shaft and the other connected to an end of the rotor to transmit driving torque to the rotor and to flex sufficiently to accommodate orbital movement of the rotor.

BACKGROUND OF THE INVENTION

This invention relates to progressing-cavity-type positive displacementhelical pumps for handling fluid, semi-fluid and comminuted material,such as the progressing cavity helical pump of my U.S. Pat. No.3,512,904. More particularly, the invention relates to an improved meansfor flexibly coupling the orbiting rotor for the pump to the rotarydrive therefor.

Progressing-cavity-type positive displacement rotary devices of thegeneral class that includes the device disclosed in my U.S. Pat. No.3,512,904 (hereinafter referred to as "Allen" devices or pumps) have arotor with an exterior helical surface that engages the surroundinginterior helical surface of the stator, the rotor surface having onemore thread than the stator surface and a lead twice that of the statorsurface. Thus, the stator surface and rotor surface define therebetweensealed pumping cavities that are axially advanced as the rotor rotatesand at the same time orbits in the same direction at two or more timesthe rate of its rotation. For a more complete description of pumps ofthis type, reference is made to my aforesaid U.S. Pat. No. 3,512,904.

This class of rotary helical devices differs from the well known Moineautype device as disclosed, for example, in U.S. Pat. No. 1,892,217. Inthe Moineau-type device the helical rotor orbits in the reversedirection relative to its rotation and the helical stator surface hasone thread more than the helical rotor.

The coupling between the Moineau rotor and drive shaft must utilize auniversal connection to accommodate the orbital motion of the rotor, theorbital speed being equal to the speed of rotation. Various types ofuniversal connections or couplings have been utilized includingconventional universal joints, long flexible tubes etc. .[.Since therotor has a cork screw shape, it is not feasible to locate the flexiblecoupling within the rotor and.]. normally coupling devices of relativelylong length are used such as those disclosed in U.S. Pat. Nos.2,512,764; 2,545,626; 2,737,119; 2,739,650 and 2,924,180.

Another technique that is used in connection with Moineau-type pumps isthe provision of a flexible mounting for the helical stator as disclosedin U.S. Pat. Nos. 2,826,152; 2,862,454 and 3,667,692. This arrangementpermits the rotor to be rigidly coupled to the rotary drive shaft andalso avoids the use of long-length universal coupling mechanisms whichgreatly add to the overall size of the device. The flexible statordesign, however, results in the stator, which is usually formed ofelastomeric material, being vulnerable to malfunction under excessivepressure since it is able to deflect in an axial direction. Also, thistype of design results in the generation of considerable heat due to theflexing of the elastomeric material and excessive heat can greatlyreduce the effective life of the stator. While this flexible mountingtechnique may be used in connection with Allen-type devices, it would bevulnerable to the same disadvantages.

One particular application for Allen pumps is in the pumping of sewagein pressure sewage systems. In these systems, it is desirable that agrinding mechanism be utilized to comminute any solid material before itenters the pumping section. Accordingly, it is desirable to use the samerotary drive shaft for both the grinder and the pump. A typical pumpingand comminuting device for use in a pressure sewage system is disclosedin U.S. Pat. No. 3,667,692. This type of device has a rotary cutterblade or grinding wheel mounted on the lower end of a vertical driveshaft below the surface of the sewage in a reservoir. Mounted on therotor shaft immediately above the grinder head is a rotary pump unitwhich may be a centrifugal type pump or in the case of U.S. Pat. No.3,667,692, a Moineau-type positive displacement pump.

In the case of the Moineau pump, since the drive shaft must extendthrough and below the rotor, the rotor is fixed to the shaft and theelastomeric stator is flexibly mounted with a flexible bellows typearrangement. In this particular application for a Moineau pump, theflexible stator arrangement must be utilized rather than a universalcoupling between the drive shaft and the rotor because the shaft mustextend through the rotor to the grinding blade unit. The flexiblemounting for the stator, however, results in the disadvantages describedabove.

The shaft-rotor universal coupling arrangement of the present inventionhas many potential uses, however, it has particular utility inconnection with the pressure sewage systems wherein it is combined witha comminutor.

SUMMARY OF THE INVENTION

It is among the objects of the invention to provide apositive-displacement-type helical pumping mechanism (e.g. Allen pump)with an improved means for coupling an orbital rotor to a rotary driveshaft.

Another object of the invention is to provide a coupling between arotary drive shaft and a hollow orbital rotor for a pump of the typedescribed wherein a universal connection is made entirely within thehollow orbital rotor.

A further object of the invention is to provide a combined rotarygrinding mechanism and a positive displacement helical pump (e.g. Allenpump) wherein both the grinder mechanism and the orbital helical rotorof the pump are driven by the same rotary drive shaft.

These and other objects are accomplished by the novel construction ofthe invention which comprises a progressing cavity, positivedisplacement, rotary pumping assembly including a rotary shaft, a rotarydrive for the shaft and a generally tubular stator coaxial with therotary shaft and having an interior helical surface. Within the statoris a cooperating tubular rotor with an exterior helical surface thatengages the interior helical surface of the stator to define therewith,sealed pumping cavities. Accordingly, as the rotor rotates and its axistranslates in an orbit circle about the axis of the drive shaft, thepumping cavities are axially advanced.

Within the rotor, in accordance with the invention, is a flexible torquetube for coupling the rotor to the shaft, the tube being connected atone end to the shaft and at its other end to an end of the rotor totransmit driving torque to the rotor and to flex in order to accommodatethe orbital movement of the rotor in an orbit circle about the axis ofthe shaft.

In the preferred embodiment, the drive shaft extends entirely throughthe helical rotor and drives at its outer end, another rotary load suchas a rotary grinder for use in comminuting solid or semi-solid materialto be pumped.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a sectional view through a sewage tank for a positive pressuresewage system that includes a grinding and pumping unit embodying theinvention;

FIG. 2 is a vertical section on an enlarged scale through the grindingand pumping unit of FIG. 1;

FIG. 3 is an elevational view from below of the grinding and pumpingunit of FIG. 2 with parts broken away for the purpose of illustration;

FIG. 4 is a cross sectional view taken on the line 4--4 of FIG. 2;

FIG. 5 is a cross sectional view taken on the line 5--5 of FIG. 2;

FIG. 6 is a cross sectional view taken on the line 6--6 of FIG. 2;

FIG. 7 is a cross sectional view taken on the line 7--7 of FIG. 2;

FIG. 8 is a cross sectional view taken on the line 8--8 of FIG. 2;

FIG. 9 is a vertical sectional view similar to FIG. 2 showing theorbital rotor after 90° of rotation from the position shown in FIGS. 2and 4 through 8;

FIG. 10 is a cross sectional view taken on the line 10--10 of FIG. 9;and

FIG. 11 is an exploded assembly view, partly in section, of the pumpingsection of the grinding and pumping unit of FIG. 9.

DESCRIPTION OF THE PREFERRED EMBODIMENT

For the purpose of illustration, the invention will be described hereinin connection with its adaption for use in a progressing cavity pump incombination with a grinder head and a submersible drive motor allmounted in a sealed sewage collection tank A. Referring to FIG. 1, thepump and grinder head assembly is identified generally by the letter B.The sewage collection tank A comprises part of a pressure sewage systemthat serves a waste generating unit and is adapted to receive sewagethat is gravity fed to the sewage collection tank A and then pumped to apreviously installed conventional gravity sewer system. As conventionalaccessories (not shown) to the unit B, a liquid level responsive on-offswitch, an overflow alarm and a discharge check valve are provided inthe sealed sewage collection tank A.

The tank A comprises a cylindrical upright wall 10, an annular coverplate 11 bolted to an annular flange at the top of the wall 10 and anannular mounting flange 12 bolted to the cover plate 11 and which servesas a mounting means for the grinding and pumping unit B. A three inchinlet pipe 13 connects to the gravity sewer line from the wastegenerating unit and a 11/2 inch discharge pipe 14 carries ground sewagefrom the grinding and pumping unit B to a conventional gravity sewersystem. The grinding and pumping unit B includes a cylindrical casing 15and a pump head 16 connected to the casing by a clamp ring 17. Thecylindrical casing 15 and pump head 16 are supported above by verticaltie bolts 18 extended downwardly through the cover plate.

Located within the cylindrical casing 15 is a cylindrical motor housing19 anchored to the pump head 16 by tie bolts 20. Electrical power leads21 for the motor (not shown) extend through the cover plate and arepreferably protected by the casing 15 from contact with sewage in thetank.

The motor has an output shaft 23 (FIG. 3) connected at a coupling 24 tothe pump shaft 25. The coupling 24 is formed of a semi-elastomericmaterial such as polyurethane to provide sufficient shock absorbingproperties and to protect the pump shaft 25 from peak loads caused byany sudden jamming of the grinder unit. The pump shaft 25 is supportedboth radially and axially by a sealed, grease lubricated ball bearingunit 22.

A cylindrical pump housing 26 with an upper flange 27 is clamped to thepump head 16 by a clamp ring 28. A housing 35 for the grinder section 30is clamped to a flange on the lower end of the pump housing 26 byanother clamp ring 29.

The grinder section broadly indicated by the numeral 30 includes acutter head 31 secured to the pump shaft by a nut 32 and having radialcutter blades 33 that cooperate with an annular stator ring 34 to grindup any semi-solid or solid material contained in the sewage being suckedupward by the pumping section 40. The stator ring 34 rests against aninwardly extending shoulder formed in the bottom of the grinder housing35 and is held in place from above by an annular spacer element 36 whichis positioned between the cutter ring 34 and the bottom flange of thepump housing 26. The spacer element 36 has inwardly extending radialribs 37 connected to an inner sleeve that supports a stabilizing bushing38 on a machined hub 39 for the cutter head 31.

The pumping section 40 comprises a positive displacement, progressingcavity helical pump such as an Allen pump adapted to pump the sewageupwardly therethrough to a discharge chamber 41 within the pump head 16and having an outlet port 42 that communicates to a fitting 43 for thedischarge pipe 14. The pump comprises a generally tubular stator 45preferably formed of rubber or other resilient material and a hollowhelical rotor 46 received within the stator. The stator 45 is presslifted into the pump housing and is clamped by means of a shoulder ateach end together with the assembly. The stator 45 may be a moldedunitary element or may be formed of two molded halves.

The rotor 46 has an exterior helical surface with a generally elipticalform as viewed in transverse cross section. The helical rotor surfacehas one more thread than the helical stator surface which it engages todefine sealed pumping cavities 47 and the threads have a lead that isequal to the number of threads in the rotor 46 times the lead of thehelical surface of the stator 45. Accordingly, as the rotor 46 rotatesand its axis translates in an orbit circle about the axis of the pumpshaft 25 the pumping cavities are axially advanced.

In accordance with the invention, the rotor 46 is coupled to the pumpshaft 25 by a flexible torque tube 50 connected at one end to the shaft25 and at the other end to the rotor 46. The tube 50 is adapted to flexas necessary in order to accommodate the orbital movement of the rotor46 in the orbit circle about the axis of the shaft 25. As indicated, thepump shaft 25 extends entirely through the helical rotor 46 and theflexible torque tube 50 is located generally within the hollow rotor andsurrounds the shaft 25. It will be seen (FIGS. 4 through 8) that thepumping cavities 47 progress from a sealed end to a maximum crosssection and then diminish to a sealing point. In the embodiment of theinvention illustrated herein, the cavities 47 extend four-fifths thelength of the rotor 46 and stator 45 or in other words, the rotor andstator are 11/4 cavity lengths long.

The rotor and stator geometry and mathematical relationships aredescribed in detail in my U.S. Pat. No. 3,512,904 which is made a parthereof and incorporated by reference herein.

A helical rotor 46 may be molded as shown in the drawing of polyurethaneor other material selected for flexibility, strength, wear and abrasionresistance and low friction characteristics. If the rotor is molded, theflexible torque tube 50 may be molded integrally with the rotor, asshown, and of the same material, the tube 50 being joined to the rotor46 at the upper portion thereof. The lower end of the tube 50 is bondedto the pump shaft 25; alternatively, the lower end of the tube 50 may bemechanically clamped to the shaft 25. If desired, the rotor may beformed from metal tubing as described in my aforesaid patent, providedwith a wear resistant coating, and then bonded to a separately formedtorque tube composed of a material having the desired physicalcharacteristics, such as high density polyurethane. As before, thelower, opposite end of the torque tube may be bonded or clamped to thepump shaft 25.

The stator 45 may be molded, for example, of BUNA-N rubber in a multiplecavity mold and clamped in place at assembly. Typical dimensions for thehelical positive displacement helical pump illustrated herein are givenin TABLE I below.

                  TABLE I                                                         ______________________________________                                        Pump                                                                          Dimension              (Inches)                                               ______________________________________                                        Eccentricity           .1                                                     Cavity length          3.2                                                    Rotor major dia        1.75                                                   Rotor minor dia        1.35                                                   Rotor form length      4.25                                                   Stator major inside dia                                                                              1.95                                                   Stator minor inside dia                                                                              1.55                                                   Stator outside dia     2.25                                                   Stator length          4.00                                                   Stator/cavity length ratio                                                                           1.25                                                   ______________________________________                                    

A pump designed to these dimensions will have a displacement of 161/2gallons per minute at a shaft speed of 1725 rpm.

The rubber stator 45 provides a semi-positive characteristic for theunit so that it is capable of being "dead ended" without risk ofbursting the lines or destroying the pump. This is an automatic safetyfeature in case of a severely blocked discharge.

While the invention has been shown and described with reference to aspecific embodiment thereof, this is intended for the purpose ofillustration rather than limitation and other modifications andvariations of the specific form herein shown and described will beapparent to those skilled in the art all within the intended spirit andscope of the invention. Accordingly, the patent is not to be limited inscope and effect to the specific form herein shown and described nor inany way that is inconsistent with the extent to which the progress inthe art has been advanced by the invention.

I claim:
 1. In a progressing-cavity, positive displacement rotary pumpassembly including a rotary shaft and drive means therefor, a generallytubular stator coaxial with said rotary shaft and having a helicallyformed interior surface with n-1 threads, a rotor located within saidstator and having a helically formed exterior surface engaging saidinterior surface of said stator to define therewith, sealed pumpingcavities, said exterior rotor surface having n threads and a lead of ntimes the lead of said interior stator surface, the improvement whichcomprises:a flexible tubular member .Iadd.surrounding at least a portionof said shaft whereby said shaft extends through said flexible tubularmember and through said rotor .Iaddend.for coupling said rotor to saidshaft, one end of said member being rigidly connected to said shaft andthe other end thereof being rigidly connected to said rotor to transmitdriving torque to said rotor and to flex to accommodate orbital movementof said rotor during rotation thereof.
 2. A submersible grinder pump forcomminuting and pumping semi-fluid material from a reservoir,comprising:a stationary housing assembly, a rotary shaft with agenerally vertical axis, a rotary drive means for said shaft operativelyconnected to the upper end thereof, rotary grinding means operativelyconnected to the lower end of said shaft for grinding and comminutingsaid semi-fluid material, a progressive-cavity, positive displacementhelical pump including a generally tubular stator mounted to saidhousing and having an interior helical surface and a hollow rotoroperatively connected to said shaft above said grinding means withinsaid stator and having a double helical surface, and a flexible torquetube extending through said rotor around said shaft, said tube beingrigidly connected at one end to said shaft and at the other end to saidrotor whereby said rotor is turned by said shaft while the rotor axismoves in an orbit about the shaft axis to define with said statoraxially advancing pumping cavities for forcing fluid material from saidgrinder portion, under pressure from said reservoir.
 3. In aprogressing-cavity, positive displacement rotary pump assembly includinga rotary shaft and drive means therefor, a generally tubular statorcoaxial with said rotary shaft and having a helically formed interiorsurface, a .Iadd.hollow tubular .Iaddend.rotor located within saidstator and having a helically formed exterior surface engaging saidinterior surface of sid stator to define therewith sealed pumpingcavities, the improvement which comprises:a .Iadd.tubular.Iaddend.flexible member .Iadd.surrounding said shaft whereby said shaftextends through said flexible member and said rotor, .Iaddend.forcoupling said rotor to said shaft, one end of said member being rigidlyconnected to said shaft and the other end thereof being rigidlyconnected to said rotor to transmit driving torque to said rotor and toflex to accommodate orbital movement of said rotor during rotationthereof.
 4. A pump assembly as defined in claim 3 wherein .[.said rotoris tubular and.]. said flexible member is located within said rotor..[.5. A pump assembly as defined in claim 3 wherein said rotor and saidflexible member are tubular and said shaft extends through said rotorand said flexible member..].
 6. A pump assembly as defined in claim.[.5.]. .Iadd.3 .Iaddend.wherein said shaft extends through and beyondsaid rotor and wherein said flexible member is positioned entirelywithin said rotor.
 7. A pump assembly as defined in claim 3 wherein.[.said rotor is tubular and.]. said flexible member is formedintegrally with said rotor.
 8. A pump assembly as defined in claim 7wherein the outer end of said shaft extending beyond said rotor isconnected to a separate rotary load, said shaft being adapted to drivesaid rotor and said separate rotary load simultaneously.
 9. A pumpassembly as defined in claim 7 wherein said flexible member is securedto said shaft adjacent the end of said rotor furthest from said drivemeans for said shaft.
 10. A pump assembly as defined in claim 9 whereinsaid rotary load is a mechanism for grinding and comminuting solid andsemi-solid material contained in the product to be pumped.